EP1624195A1

EP1624195A1 - Axial pump

Info

Publication number: EP1624195A1
Application number: EP05015556A
Authority: EP
Inventors: Takanori Hitachi Ltd. Intell.Prop.Group Ishii; Ryuichiro Hitachi Ltd. Intell.Prop.Group Iwano; Akira Hitachi Ltd. Intell.Prop.Group Manabe; Yasuhiro Hitachi Ltd. Intell.Prop.Group Inoue
Original assignee: Hitachi Ltd; Hitachi Plant Technologies Ltd; Hitachi Industries Co Ltd
Current assignee: Hitachi Ltd; Hitachi Plant Technologies Ltd
Priority date: 2004-08-04
Filing date: 2005-07-18
Publication date: 2006-02-08
Anticipated expiration: 2025-07-18
Also published as: DE602005015279D1; US20060029495A1; EP1624195B1; JP4590227B2; US7604458B2; JP2006046168A

Abstract

The guide vanes (3) comprise two kinds of guide vanes which are alternately placed around the angular direction. One kind of the guide vanes has a longer length than the other kinds of the guide vanes at the region which is close to the surface of the hub. However, at the region which is close to the shroud (4) the guide vanes substantially have the same length. The leading edges of the second kind of guide vanes are located further downstream of the pump axial direction than the first kind of guide vanes.

Description

FIELD OF INVENTION

The present invention relates to an axial flow pump and a diagonal flow pump, especially, those that have plural impellers and plural guide vanes placed in the back stream of the impellers.
Axial-flow pumps generate rotational energy in the fluid by means of the impellers thereof and convert the rotational energy to the static pressure by means of guide vanes placed in the back flow of the impellers. Usually, the impellers and the guide vanes have the same physical shape of vanes and are mounted to the axis and/or the casing in uniformly same separation. The flow at the outlet of the impellers has a flow component along a rotational axis and an angular component which is called as a rotational component, hereinafter. The guide vanes are mounted in such a configuration that the leading edges of the vanes are compliant to the axial angle of the rotational component of the back flow generated by the impellers. Since the flow condition of the fluid flow coming out from the impellers depends on the flow volume, the guide vanes are set in a single operating condition which is for a particular flow volume. The design such as, for example, the angles α and γ are same in the configuration shown in FIG. 7 is to maximize the conversion from the rotational energy to the static pressure with such a particular flow volume.
The guide vanes are set such that the setting condition is optimized for a single particular operating condition. The reference shows guide vanes that have the same shape in the axial symmetry and provide an optimized performance for a certain condition.

BRIEF SUMMARY OF THE INVENTION

One of the important performances required for the fluid pump is efficiency. Since pumps are operated under various conditions of flow volume and high efficiency is required not only for a single specific condition but also for other different conditions of flow volume. In the best performance of the guide vanes, the flow coming out from the impellers flows along the guide vanes and the rotational component of the flow is converted into static pressure at the stage of the flow passing by the guide vane. Since the cross sectional flow distributions such as those close to the hub of the vanes and those close to the shroud are different due to the difference of the rotational flow volume at the outlet of the impeller, the cross sectional shape of the vane in the region close to the hub is more declined than that of the vane in the region close to the shroud. Since the flow rate of the flow passing direction in the region close to the hub becomes small in a view of cross section when the flow volume becomes small, the angle α of the flow which comes into the guide vanes is smaller than the angle for the optimum flow volume operation and the flow direction at the leading edges of the guide vanes and the direction of the guide vanes are deviated. Accordingly, the flow is separated at the leading edges of the guide vanes and the vortexes caused by the separation are pushed out to the downstream from the leading edges of the guide vanes. Since this vortexes choke up the flow paths generated between any adjacent two guide vanes axially set around and work as a resistance against the flow so that the total performance of the pump becomes worse. On the other hands, the component of the flow passing direction of the flow rate becomes large and the angle of the flow at the leading edges of the guide vanes is deviated when the operation is done for larger flow volume than the optimum condition. The direction of the flow are deviated in the reverse direction against the direction of the flow in case when the flow volume is small and therefore the separation is generated at the leading edges of the guide vanes in a reverse side so that the vortexes of the separation choke the flow paths up and reduce the pump performance. The separation distance between adjacent guide vanes in the cross sectional plane is shorter in the region close to the hub and longer in the region close to the shroud due to the smaller radius the region closer to the hub and therefore the effect of choking up of flow paths due to the existence of the separation vortex is particularly a serious problem.
The purpose of the present invention is to minimize the degradation of the performance due to the separation vortex generated at the leading edges of guide vanes by means of flow volume changes and to provide an axial flow pumps and diagonal flow pumps that can maintain high performance in the wide range of operation condition from a small flow volume to a large flow volume.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic that shows a structure of impellers and guide vanes of an axial flow pump of an embodiment regarding to the present invention.
FIG. 2 is a schematic that shows a right half of a cut view of an axial flow pump in a plane including the pump rotation axis.
FIG. 3 is a schematic that shows a cut view of impellers and guide vanes cut by a cylinder coaxial to the pump rotation axis in the region close to the hub.
FIG. 4 is a schematic that shows a cut view of impellers and guide vanes cut by a cylinder coaxial to the pump rotation axis in the region close to the shroud.
FIG. 5A is a schematic that shows a projection view of a short guide vane in the circle direction.
FIG. 5B is a schematic that shows a cut view of a guide vane cut by three kinds of cylinders A1, C1 and B1 coaxial to the pump rotation axis: A1 has the radius close to the hub, C1 to the shroud and B1 intermediate radius therebetween.
FIG. 6A is a schematic that shows a projection view of a long guide vane in circle direction.
FIG. 6B is a schematic that shows a cut view of a guide vane cut by three kinds of cylinders A2, C2 and B2 coaxial to the pump rotation axis: A2 has the radius close to the hub, C2 to the shroud and B2 intermediate radius therebetween.
FIG. 7 is a schematic that shows cross sectional flows of the fluid in the region close to the hub under an optimum flow volume regarding convention axial pumps.
FIG. 8 is a schematic that shows cross sectional flows of the fluid in the region close to the shroud under an optimum flow volume regarding convention axial pumps.
FIG. 9 is a schematic that shows cross sectional flows under the condition that the flow crossing the cross section area of the region close to the hub is in small flow volume regarding conventional axial pumps.
FIG. 10 is a schematic that shows cross sectional flows under the condition that the flow crossing the cross section area of the region close to the hub is in large flow volume regarding to conventional axial pumps.
FIG.11 is a schematic that shows cross sectional flows under the condition that the flow crossing the cross section area of the region close to the hub is in small flow volume regarding axial pumps of the present invention.
FIG. 12 is a schematic that shows cross sectional flows under the condition that the flow crossing the cross section area of the region close to the hub is in large flow volume regarding to axial pumps of the present invention.
FIG. 13 is schematic that shows an embodiment wherein three kinds of vanes are periodically set.
FIG. 14 is a schematic that shows an embodiment of a diagonal flow pump to which the present invention is applied.

DETAILED DISCRIPTION OF THE INVENTION

(1) In order to achieve the above purpose, the present invention provides an axial pump wherein a plurality of some of guide vanes is set in the back flow of the plurality of impellers and the leading edges of the part of the guide vanes are placed in the downstream regarding to the pump rotation axis direction so that the plurality of the vanes which have different shapes from those of the other vanes are placed around the angular direction.
A plurality of some of guide vanes is set in the downstream of the plurality of the impellers and the area of the inlet to flow path to guide vanes becomes large. Since the effective area of the inlet to the flow path to guide vanes becomes large in the operation conditions other than the optimum condition, the performance degradation due to the separation vortexes generated at the leading edges of the guide vanes can be minimized and the high performance pump covering the wide range of operation condition from the small flow volume to the large flow volume.
(2) In order to achieve the above purpose, the present invention provides an axial flow pump that has a plurality of impellers and a plurality of guide vanes set in the back flow of the plurality of the impellers wherein the pump has plural kinds of guide vanes regularly around the angular direction the in the downstream of the impellers so that some of the guide vanes have the leading edges of the guide vanes placed further in the down stream rather than the other guide vanes.
According to this configuration, as explained in (1), the performance degradation due to the separation vortexes generated at the leading edges of the guide vanes can be minimized and the high performance pump covering the wide range of operation condition from the small flow volume to the large flow volume since the area of the inlet of the flow to flow path to guide vanes becomes large.
(3) Another variation of the invention is that the plurality kinds of the guide vanes are provided by the first plurality of guide vanes and the second guide vanes which have shorter vane length in the flow direction in comparison to the first guide vanes and the leading edges of the second guide vanes locate further downstream in comparison to the leading edges of the first guide vanes, preferably in addition to the variations described by (1) and (2).
(4) Another variation of the invention is that the plurality of the second guide vanes have shorter vane lengths in the region close to the pump rotational axis than in the region far from the pump rotation axis and the vane lengths in the region close the pump rotational axis are shorter than the first guide vanes in the direction of the pump rotation axis, preferably in addition to the variations described by (3).
(5) Another variation of the invention is that the plurality of the second guide vanes have shorter vane lengths in the in the pump axial direction as closer to the pump rotation axis and the vane lengths in the region close the pump rotational axis are shorter than the first,guide vanes in the direction of the pump rotation axis, preferably in addition to the variations described by (3).
(6) In order to achieve the above purpose, the present invention provides a diagonal flow pump wherein a plurality of some of guide vanes is set in the back flow of the plurality of impellers and the leading edges of the part of the guide vanes are placed in the downstream regarding to the pump rotation axis direction so that the plurality of the vanes which have different shapes to the other vanes are regularly placed around the angular direction.
Accordingly, as explained in (1), since the effective area of the inlet to the flow path to guide vanes becomes large in the operation conditions other than the optimum condition, the performance degradation due to the separation vortexes generated at the leading edges of the guide vanes can be minimized and the high performance pump covering the wide range of operation condition from the small flow volume to the large flow volume.
(7) In order to achieve the above purpose, the present invention provides an diagonal flow pump that has a plurality of impellers and a plurality of guide vanes set in the back stream of the plurality impellers wherein the pump has plural kinds of guide vanes regularly around the angular direction the in the back flow of the impellers so that some of the guide vanes have the leading edges of the guide vanes placed further in the downstream rather than the other guide vanes.

According to this configuration, as explained in (1), the performance degradation due to the separation vortexes generated at the leading edges of the guide vanes can be minimized and the high performance pump covering the wide range of operation condition from the small flow volume to the large flow volume since the area of the inlet of the flow to flow path to guide vanes becomes large.
According to the present invention, it is possible to minimize the degradation of the performance due to the separation vortex generated at the leading edges of guide vanes by means of flow volume changes and to realize an axial flow pumps and diagonal flow pumps that can maintain high performance in the wide range of operation condition from a small flow volume to a large flow volume.
The embodiments of the present invention are explained by using drawings.
As shown in FIG. 1, the axial flow pump has a plurality of impellers 2 and a plurality of guide vanes 3 which are placed in the back flow of the impellers 2, both of which are housed in a shroud 4. The impellers 2 are fixed to the rotation shaft 6 and the impellers 2 start to rotate with the rotational axis X of the rotation shaft 6 which is driven to rotate by a motor (not shown in the figures) coupled to the rotation shaft 6. The leading edges of the impellers 2 facing to the shroud 4 are not fixed to the shroud 4. On the other hand, the guide vanes 3 do not rotate themselves but the leading edges of guide vanes 3 close to the pump rotation axis X are fixed to a guide vane hub 7 which surrounds the rotation shaft 5 and the other leading edges far from the pump rotation axis X are fixed to the shroud 4. The letter "F" in FIG. 1 and 2 shows the flow velocity vector of the fluid.
FIG. 3 and FIG. 4 show the cross sectional views of the impeller 2 and the guide vanes 3 cut by a cylinder which is coaxial to the pump rotation axis X. FIG. 3 shows the cross sectional views in the region close to the hub 7 and FIG. 4 to the shroud 4.
As shown in FIG. 3 and FIG. 4, the guide vanes 3 comprise two kinds of guide vanes 11 and 12 which are alternatively placed around the angular direction. The guide vanes 12 have longer length than the other guide vanes 11 at the region which is close to the surface of hub but have substantially same lengths as the other guide vanes 12 at the region which is close to the shroud. The leading edges of the guide vane 11 locate in the down stream of the pump axial direction. The letter "R" denotes the rotation direction.
FIG. 5A and FIG. 6A show cross sectional views of the guide vanes 11 and the guide vanes 12 in the pump rotation direction, respectively. The cylinder surfaces A1, B1 and C1 are defined from that close to the hub 7 and to that the shroud 4 in FIG. 5A. The same cylinder surfaces are denoted by A2, B2 and C2 in FIG. 6A. The cylinder surfaces A1 and A2, B1 and B2 and C1 and C2 are identically same. FIG. 5B and 6B show the cross sectional views projected to these cylinders.
The guide vanes regarding the present invention satisfy the following two conditions.

(1) the length of the guide vanes 11 provides the relation; (length of the guide vanes 11 cut by the cylinder A1) < (length of the guide vanes 11 cut by the cylinder B1) < (length of the guide vanes 11 cut by the cylinder C1)
(2) the relation between the length of the guide vanes 11 and the length of the guide vanes 12 provides the relation; (length of the guide vanes 11 cut by the cylinder A1) < (length of the guide vanes 12 cut by the cylinder A2)
and
(length of the guide vanes 11 cut by the cylinder B1) < (length of the guide vanes 12 cut by the cylinder B2)
and
(length of the guide vanes 11 cut by the cylinder C1) < (length of the guide vanes 12 cut by the cylinder C2)

As for the guide vanes 11 which have short vane lengths, the guide vanes keep the relation that the closer to the pump rotation axis shorter the shorter the vane length. As for the guide vanes 12 which have long vane lengths, the dependency to the radial direction of the rotation axis regarding the vane lengths such as the region crossing with the cylinder A2, B2 and C2 can be arbitrarily determined.
The effect of the present invention is discussed as follows.
One of the important performances required for the axial flow pumps is efficiency in terms of how less of the flow kinetic energy is lost in the fluid flow.
In the operation condition that serves the maximum performance of the conventional guide vanes (wherein the maximum performance implies no generation of separation vortexes so that flow kinetic energy lost in the fluid dynamics is small) , the regional flows of the fluid of the convention axial pumps are depicted in the FIG. 7 and 8 which show the cross sectional views cut in a cylindrical surface coaxial to the pump rotational axis. FIG. 7 shows the cross sectional flows in the region close to the hub and FIG. 8 shows the cross sectional flows in the region close to the shroud. The flows generated by the impeller 102 pass though and along the guide vanes 103 and the rotation component of the flow is effectively converted to the static pressure while the flow is passing through the guide vanes 103. Since the cross sectional flow distributions such as those close to the hub of the vanes and those close to the shroud are different due to the difference of the rotational flow volume at the outlet of the impeller, the cross sectional shape of the vane in the region close to the hub is designed to be more declined than that of the vane in the region close to the shroud. More specifically, the angle α shown in Fig. 7 is smaller than α 8 in FIG. 8. When the tip angles γ and γ 8 at the hub and the shroud which are aligned to the angles of the flow, respectively, are compared, then γ becomes smaller than γ8.
FIG. 7 especially shows the flow volume condition that the no separation vortexes are generated at the tips of the guide vanes, which is defined as the "optimum flow condition". This condition can be depicted that the tangential line extended to the inlet cross sectional plane (P1) which is normal to the pump axial line has an angle γ thereto. For this optimum flow condition, the flow has a relation such as α= γ.
The angle α changes in accordance with the change of the flow volume. The flow volume is defined by the product of the cross sectional area of the flow and the projection of the flow velocity vector F. The component in the pump rotation plane is F3. For non-compressive flow, the flow volume across any cross sectional area is constant therefore the relation:
Flow volume measure at the impeller inlet

= Product of the inlet cross section area of the impeller and the projection of the flow velocity vector F at the impeller inlet P0
= Product of the outlet cross section area of the impeller and the projection of the flow velocity vector F2 at the impeller outlet P1
= Product of the outlet cross section area of F3
= Flow volume measured at impeller outlet

On the other hand, the component of F2 in the plane normal to the pump rotation axis is F4 and the rotation velocity in the flow rotating around the pump axis wherein the rotation velocity is added by the impeller rotation. According to this definition, the vector F and F3 changes in their magnitudes. When the flow volume increases by 10% then F3 does by 10%. Generally the impellers rotate in a constant rotation speed. The rotation component of the flow volume added by the impeller rotation at the impeller outlet does not largely change at the optimum flow condition. Therefore, F4 does not largely change at the impeller outlet against the increase and decrease of the flow but F3 does so that the angle α changes. This concludes that α becomes large and small when F3 becomes large and small, respectively.
FIG. 9 shows the flows under the condition that the flow crossing the cross section area of the region close to the hub is in small flow volume. When the flow volume becomes less, the flow rate to the direction of the flow path becomes small, the angle α 9 of the flow entering to guide vanes 103 becomes smaller than that in the optimum flow volume condition, that is α shown in FIG. 7. The flow direction at the leading edge of the guide vanes 103 and the direction of guide vanes 103 are deviated. Therefore the flow generates separation at the leading edge of the guide vanes 103 and the vortexes 110 caused by the separation are pushed away from the leading edges of the guide vanes 103 to the down streams. These vortexes 110 "choke up" the flow paths between two adjacent guide vanes 103 in the cross section and work as a resistance against the flow. In other words, the width of the flow path becomes narrow from W1 to W2. Therefore the overall pump performance is reduced.
The "choke up" of the flow is explained as follows. The vector F3 is smaller for the case shown in Fig. 7. The vortexes 110 are generated and their width is W5. In relation to Fig. 7, the following relation: $W 1 = W 2 + W 5$

can be obtained. Since the shapes of the guide vanes are same as those shown in FIG. 7, the interval between the adjacent vanes is constantly W1. FIG. 7 shows that the fluid flows from the inlet of the guide vanes to the outlet of the guide vanes. However the flow is turned into the separation vortexes 110 in the region close to the guide vanes and the fluid stays in the separation vortexes. The flow is appeared that the fluid travels from the inlet of the guide vanes the outlet through the channel shows W2. Since the interval between the guide vanes is W1 and the separation vortex "chokes" the channel to a width of W5. Though the physical width of the channel is W1, the flow total volume is mainly determined by the channel excluding the vortex with W5 and the effective flow path is defined by the width W2.
On the other hands, FIG. 10 shows the flow when the operation is done for larger flow volume than the optimum condition. The component of the flow passing direction of the flow rate becomes large and the angle of the flow at the leading edges of the guide vanes 103 is deviated. The direction of the flow are deviated in the reverse direction against the direction of the flow in case when the flow is in small flow volume and therefore the separation is generated at the leading edges of the guide vanes 103 in a reverse side as shown in FIG. 9 so that the separation vortexes choke the flow paths up and the effective flow path width is reduce to W6 as shown in FIG. 10. This results into the reduction of the pump performance. Since the radius in the region close to the hub is smaller than that to the shroud, the gap between two adjacent guide vanes become to be narrowed into W1 from W6 by the width W7 of the separation vortex (in other words, the area of the flow path at the inlet to the guide vanes) , the influence of choking the flow path by the separation vortexes is a particular problem.
The details of the large volume flow are explained. The width of the separation vortex is W7, then the width W6 of the channel of the flow becomes W6 = W1- W7. The narrower the channel of the flow is, the larger the flow velocity is. Therefore the viscous resistance becomes large when the channel of the flow becomes narrow and flow energy is large lost. Therefore it is preferred the wide flow path width for the purpose of reducing the flow energy lost.
FIG. 11 shows the flow of the present invention, particularly the flow in the cross section in the region close the hub when the operation is done for small flow volume than the optimum condition. Due to the short length of the vanes in the regions close to the hub, the flow path width at the leading edges of the guide vanes 12 is enlarged to be W4 (in other words, the area of the inlet to the flow path of the guide vanes is enlarged), it can be understood that the effective area of the flow patch at the inlet to the guide vanes. By this configuration of vanes, the chock up of the flow path W4 due to the generation of separation vortexes 110 caused by the angle α becoming small is less effective and the degrading of the performance is suppressed.
For this low condition, the detail is explained as follows. There are two separation vortexes over the three adjacent vanes. For the conventional configuration, the width of the effective flow path is W2+W2 (=W1+W1-W5-W5). However for the present invention, only one separation vortex is generated and a width (WB) of one guide vane is removed in the channel of the flow and therefore the effective flow path is W4 (=W1+W1-W5-WB). The present invention can widen the width of the effective flow path by the dimension as much as W5+WB. Therefore the present invention provides less flow resistance and less flow energy lost.
FIG. 12 shows the flow under a condition such that the flow crossing the cross section area of the region close to the hub is in large volume. The flow angle α 12 shown in FIG. 12 which is for large flow volume is larger than α shown in FIG. 7, the particular locations where the separation vortexes are generated are different for the cases shown in FIG. 12 and FIG. 11. The separation vortexes 110 are generated in the reverse side for the case when the flow volume is small but the reduction of the flow path width W4 is suppressed in the same reduction as in the case that the flow volume is small.
The details of the large flow volume are explained. The width of the effective flow path (in other word, a flow channel) can be widened by a dimension as much as W7 + WB since it is W8 (=W6+W6+W7+WB) in comparison to the conventional guide vane configuration. For the present invention, there is no separation vortexes generated for the optimum flow condition similar to the condition shown in FIG. 7 and the flow energy loss becomes small since the quantities of the separation vortexes is less generated for the flow conditions either over or under the optimum conditions.
The cross sectional view of the guide vanes 3 cut by a cylinder which is close to the shroud 4 is same as the guide vanes in the length in angular direction. According to the facts that average flow path width W at the shroud is larger than that at the hub along the angular direction and the separation vortexes are less generated for the change of flow volume since the flow angle at the leading edges in the region close to the shroud is less keen than that at the leading edges in the region close to the hub, the conventional guide vanes do not provide a merit by shortening the lengths of some of the vanes. Actually, the variance of the flow angle is small for the case when the flow volume vary because the flow angle in the region close to the shroud is large and therefore separation vertexes are scarcely generated in the region close to the shroud even the separation vortexes are generated in the region close to the hub so that the choke up of the flow paths due to the separation vortexes are not generated in the most cases. Considering the original purpose of the guide vanes 3, which is to convert the rotational flow component to static pressure in high efficiency, it is concluded that the longer the length of the guide vanes in the region close to the shroud the better the performance.
As discussed before, since the present invention provides the effect that the area of the inlet to flow path to guide vanes 11 and 12 is enlarged to W4 so that the effective area of the inlet to flow path to the guide vanes 11 and 12 can be enlarged in the operation conditions other than that for the optimum flow volume, the degradation of the performance due to the separation vortexes generated in the leading edges of the guide vanes following to the change of the flow volume can be suppressed into a minimum level and the high performance pump covering the wide range of operation condition from the small flow volume to the large flow volume can be realized.
FIG. 13 shows an example that uses three kinds guide vanes 21, 22 and 23 which have different lengths and regularly placed around the angular direction. In comparison to the case wherein two kinds of guide vanes are used, the average flow path width only at the inlet to the guide vanes can be effectively enlarged.
The guide vanes regarding the present invention can be adopted by other types of pumps. FIG. 14 shows an example applied to a diagonal flow pump. The diagonal flow pump has a plurality of impellers 32 and a plurality of guide vanes 33 which are placed in the back flow of the impellers 32, both of which are housed in the shroud 34. The impellers 32 are linked with the rotation shaft 36 and the impellers 33 start to rotate with the rotational axis X of the rotation shaft 36 which is driven to rotate by a motor (not shown in the figures) coupled to the rotation shaft 36. The edges of the impellers 32 facing to the shroud 34 are not fixed to the shroud 34. On the other hand, the guide vanes 33 do not rotate themselves but the leading edges of guide vanes 33 close to the pump rotation axis X are fixed to a guide vane hub 37 which surrounds the rotation shaft 5 and the other leading edges far from the pump rotation axis X are fixed to the shroud 34.
For the diagonal flow pumps, the cross sectional shapes of the guide vanes 33 cut in the rotational surface 38 which is shown by a dotted line in FIG 14 is preferably similar to the cross sectional shapes as shown in FIG. 3. In other words, a plurality of guide vanes 33 are set in the downstream of the plurality of impellers and the leading edges of the some guide vanes are placed in the downstream regarding to the pump rotation axis direction compared to the those of the other guide vanes by the configuration that the plurality of the some guide vanes which have different kinds of guide vanes (for example, two kinds of guide vanes similar to the guide vanes 11 and 12) as different shapes or different lengths to the other vanes are regularly placed around the angular direction.
By means of this embodiment of the present invention, the similar effect to the axial flow pumps regarding the high efficiency performance in wide range of flow volume around the optimum condition can be obtained for the diagonal flow pumps as well.

Claims

An axial flow pump comprising a plurality of impellers (2) and a plurality of guide vanes (3) which are fixed to a shroud (4) and arranged downstream of said impellers, wherein
said plurality of guide vanes comprise plural kinds of guide vanes one of which having a shape different from the other kinds of guide vanes, and are arranged regularly around an angular direction such that leading edges of said one kind of guide vanes are arranged further downstream than leading edges of said other kinds of guide vanes.
An axial flow pump comprising a plurality of impellers (2) and a plurality of guide vanes which are fixed to a shroud (4) and arranged downstream of said impellers, wherein
plural kinds of guide vanes, one of which having a length different from the other kinds of guide vanes, are regularly arranged around an angular direction such that leading edges of said one kind of guide vanes are arranged further downstream than leading edges of said other kinds of guide vanes.
The pump of claim 1 or 2, wherein two kinds of guide vanes, a first kind and a second kind, are included such that leading edges of said second kind of guide vanes are shorter than leading edges of said first kind of guide vanes in a direction of the pump rotation axis and said leading edges of said second kind of guide vanes are arranged further downstream than said leading edges of said first kind of guide vanes.
The pump of claim 3, wherein said second kind of guide vanes has a shorter length in a region close to the pump rotation axis than the length in a region farther from said pump rotation axis along the direction of said pump rotation axis and said second kind of guide vanes have a shorter length than said first kind of guide vanes in a region close to the pump rotation axis along the direction of said pump rotation axis.
The pump of claim 4, wherein said second kind of guide vanes have a configuration such that the shorter the length the closer to the region of said pump rotation axis and said second kind of guide vanes have a shorter length than said first kind of guide vanes in a region close to the pump rotation axis along the direction of said pump rotation axis.
A diagonal flow pump comprising a plurality of impellers (2) and a plurality of guide vanes which are fixed to a shroud (4) and arranged downstream of said impellers, wherein
plural kinds of guide vanes, one of which having a shape different from the other kinds of guide vanes, are regularly arranged around an angular direction such that leading edges of said one kind of guide vanes are arranged further downstream than leading edges of the other kinds of guide vanes.
A diagonal flow pump comprising a plurality of impellers (2) and a plurality of guide vanes which are fixed to a shroud (4) and arranged downstream of said impellers, wherein
plural kinds of guide vanes one of which having a length different from the other kinds of guide vanes, are regularly arranged around an angular direction such that leading edges of said one kind of guide vanes are arranged further downstream than leading edges of said other kinds of guide vanes.